Method for controlling vehicle dynamics

ABSTRACT

Using a model calculation, desired changes in the yaw rate Δφ and the transverse acceleration Δy are determined from a small change actually made in the steering angle and are compared to measured quantities Δφ F  and Δy F  determined on the vehicle. The deviations of the actual values of yaw rate and transverse acceleration from the calculated values are weighted using predetermined weighting factors for the relative importance of yaw rate and transverse acceleration and supplied with factors dependent on the individual wheel; finally, the values relating to the same wheel are added. They represent desired changes in the brake slip values and a controller finally converts these into brake slip value changes.

BACKGROUND OF THE INVENTION

As is known, vehicle dynamics are influenced by the forces exerted on the tires of the vehicle by the roadway. It is known that, when the vehicle is braking, the skew running stiffness of the tires depends on the brake slips of the tires. In general, the skew running stiffness of the tires decreases with increasing brake slip.

For guiding the vehicle, cornering forces on the tires are necessary. For the yawing dynamics of the vehicle, yawing moments on the vehicle are necessary. These yawing moments can be caused both by the braking forces and by the cornering forces. For the yawing movement of the vehicle, the braking forces are thus important for two reasons. Firstly because the braking forces can exert a yawing moment on the vehicle and secondly because the braking forces can influence the yawing moment of the cornering forces (indirectly via the brake slip) by changing the skew running stiffness.

SUMMARY OF THE INVENTION

It is an object of the present invention to provide a method of controlling vehicle dynamics.

The driving dynamics are thus influenced by means of brake intervention. The driving dynamics are optimized during a braking operation yet the braking distance is also minimised.

For this purpose, it is necessary to seek a compromise in which the brake slip values at the tires are set in such a way that, on the one hand, the yawing dynamics are improved without, on the other hand, wasting too much braking retardation. For this purpose, it is determined at each tire how, on the one hand, the yawing moment on the vehicle changes and how, on the other hand, the braking retardation of the vehicle changes when there is a small change in the brake slip. The ratio of the change in the yawing moment to the change in the braking retardation is calculated for each wheel. For control of the yawing moment, the wheel with the largest ratio is used most and the wheel with the smallest ratio is used least. This settles the central question of how the distribution of the braking forces or the distribution of the brake slips is to be configured.

The change in the braking and cornering forces due to changes in the brake slips can either be measured directly or estimated by suitable estimating algorithms.

For the determination of the necessary brake slip changes at the wheels, a control deviation is required. A model-based follow-up control is chosen for this purpose. Since, however, the position of the vehicle cannot immediately be measured, only the transitional behavior of the vehicle transverse acceleration and vehicle yawing speed is simulated. The damping of the systems is to be critical since this is considered the best dynamic behavior by most drivers.

For the following description, the notation given in FIG. 1 and on page 9 applies.

The model is described as follows:

    Δφ+k.sub.1 ·Δφ+k.sub.2 Δφ=k.sub.5 ·Δδ                                  (I)

    Δy+k.sub.3 ·Δy+k.sub.4 Δy=k.sub.6 ·Δδ                                  (II)

k₅ and k₆ can be determined from steady-state cornering (where δ=1/R).

They are obtained from the following calculation ##EQU1## If the Ackermann condition δ=1/R is made less severe, i.e. δ=k_(a) ·1/R, k_(a) >1,) the following applies: ##EQU2## The model is therewith established. The handling can be influenced via the parameters k₁, . . . , k₄, k_(a).

In the Ackermann diagram, the line ##EQU3## intersects the curves at their maximum when k_(a) ≈2.

In order to effect the changes in φ and y, changes must be introduced into the horizontal tire forces:

    ΔB.sub.1 to ΔB.sub.4, ΔS.sub.1 to ΔS.sub.4

The following equations apply: ##EQU4##

As a possible variation, there are the wheel brake-slip values of the four wheels. However, to ensure that as little braking retardation as possible is wasted, the slip values must be chosen so that ΔB₁ +ΔB₂ +ΔB₃ +ΔB4 is approximately at its maximum, i.e. that the sum of the braking force reductions is at its minimum.

The values for ΔB₁. . . ΔB₄ can be calculated from the stability reserve, while ΔS₁. . . ΔS₄ can be calculated from the transverse stability reserve, it being possible to vary the stability reserves via the wheel brake slip.

For the purpose of further consideration, the above relations are transformed as follows: ##EQU5## Δy can be varied by changes in ΔB₁. . . ΔB₄. The same applies to Δφ and Δx. Since the sum of the ΔB_(i) should be kept as small as possible, it is right to change only the B_(i) with the largest coefficient. It is also the case that the ΔB_(i) do not make an equal contribution to the vehicle retardation. In order to judge which coefficient in the first two relations given above is largest, allowing for the requirement that |Δx| should be kept to a minimum, the coefficients of the first two relations should be divided by the corresponding coefficient of the third relation. This corresponds to a weighting of the coefficients for the optimization of the braking retardation.

Since the coefficients vary with time and change continuously relative to one another due to the controller correction, it is advisable to alter all the ΔB_(i) but only to the extent that this corresponds to their weighted coefficients.

Transformation gives: ##EQU6##

Since, in general, the slip curve does not rise monotonically, the relationship between ΔS_(i) and ΔB_(i) is not unambiguous. It is therefore better to consider the changes in B_(i) and S_(i) as a function of the control variables λ_(i).

In general, the following applies: ##EQU7## further changes due to movement of the vehicle body and axle movement not being taken into account.

Since the change in the slip, Δλ_(i), has a greater bandwidth than the other changes ΔY, Δφ and ΔX, these changes are neglected. These dynamic components can be allowed for at a later stage by the inclusion of D and I components in the controller.

The following thus remains: ##EQU8##

Using these, it is then possible to set up equations for the changes in the desired slips at the wheels, thus for example: ##EQU9##

The values ##EQU10## are obtained from stored tire characteristic diagrams or from models which simulate the tire characteristic diagrams or directly from measurements by changing the slip by Δλ_(i), measuring the force changes ΔS_(i) and ΔB_(i) and setting ##EQU11##

The following is finally obtained, in abridged notation: ##STR1##

By the choice of values for the coefficients C₁ and C₂ it is possible to determine which is more important: control of the deviation of the transverse acceleration (Δy-Δy_(F)) or control of the deviation of the yaw rate (Δφ-Δφ_(F)).

To compensate for the neglect of the dynamic components ΔY and Δφ, the following is proposed.

Instead of processing the deviations alone, the processing of the differentials and integrals of the deviations can also be included. A PD or PI or PID controller is then obtained; e.g. the relation for Δλ₁ in the case of PID control is as follows:

BRIEF DESCRIPTION OF THE DRAWING

The objects, features and advantages of the present invention will now be illustrated in more detail by the following detailed description of a preferred embodiment of the invention, reference being made to the accompanying drawing in which:

FIG. 1 is diagrammatic plan view of a motor vehicle having four tires illustrating the braking forces B_(i) and cornering forces S_(i) on the tires and the steering angle variable for the front tires; and

FIG. 2 is a flow chart of a preferred embodiment of the method of controlling vehicle dynamics according to the invention.

DETAILED DESCRIPTION OF A PREFERRED EMBODIMENT

An illustrative embodiment of the invention is explained with reference to FIG. 2 of the drawing.

The brief changes in the steering angle Δδ and the longitudinal velocity V_(x) of the vehicle performed from time to time are input into blocks 1 and 1' respectively and Δδ is there multiplied by K₂ V_(x) /K_(a) l and K₄ ·V_(x) ² /K_(a) ·l respectively. By means of integrators 2, 3 and 2', 3' respectively, multipliers 4, 5 and 4', 5' respectively and adders 6 and 6' respectively, the quantities Δy and Δφ of the model are obtained at the output of the integrators 3 and 3'.

In comparators 7 and 7' respectively, the model quantities Δy and Δφ are compared to the corresponding quantities Δy_(F) and Δφ_(F) measured on the vehicle. The deviations (Δy-Δy_(F)) and (Δφ-Δφ_(F)) are provided in multipliers 9 and 9' respectively with weighting factors c₁ and c₂ respectively. Each half of the system then separates into four channels and the weighted deviations are multiplied in multipliers 10 and 10' respectively by factors P_(yi) and P.sub.φi assigned to the individual wheels. Signals associated with the same wheel are then added in adders 11 and the desired changes of the slips Δλi of the individual wheels are obtained. These changes are passed to controllers 8a contained in the vehicle block 8 and these controllers alter the brake pressure in such a way that the currently prevailing brake slip λi is converted into a new brake slip λi+Δλi. For this purpose, the brake slip must, in a known manner, be determined and compared to the new desired brake slip Δi+Δλi. The brake pressure variation is ended when the brake slip has come to equal the desired brake slip. If, instead of Δλi, signals corresponding to the desired braking force changes ΔBi are to be produced and corresponding braking force changes are to be performed by the controllers, then, in FIG. 2, all that is required is to specify different factors P'_(yi) and P'.sub.φi respectively in multipliers 10 and 10' respectively.

While the invention has been illustrated and described as embodied in a method of controlling vehicle dynamics, it is not intended to be limited to the details shown, since various modifications and structural changes may be made without departing in any way from the spirit of the present invention.

Without further analysis, the foregoing will so fully reveal the gist of the present invention that others can, by applying current knowledge, readily adapt it for various applications without omitting features that, from the standpoint of prior art, fairly constitute essential characteristics of the generic or specific aspects of this invention. 

What is claimed is new and desired to be protected by Letters Patent is set forth in the appended claims.
 1. A method of controlling brake slip at each of n tires of a vehicle during braking to control driving dynamics, said method comprising the steps of:a) making a small change Δδ in steering angle of the vehicle; b) performing a model calculation to obtain a calculated yaw rate Δφ and a calculated transverse acceleration Δy using the following model differential equations:

    Δφ+k.sub.1 Δφ+k.sub.2 Δφ=k.sub.5 ·Δδ                                  (I)

    Δy+k.sub.3 Δy+k.sub.4 Δy=k.sub.6 ·Δδ(II)

wherein k₁ to k₄ are constants and k₅ and k₆ are quantities dependent on vehicle speed; c) measuring an actual yaw rate Δφ_(F) and an actual transverse acceleration Δy_(F) ; d) comparing the actual yaw rate and calculated yaw rate and determining a deviation of the calculated yaw rate from the actual yaw rate Δφ-Δφ_(F) ; e) comparing the actual transverse acceleration and the calculated transverse acceleration and determining a deviation of the calculated transverse acceleration from the actual transverse acceleration Δy-Δy_(F) ; f) calculating changes in brake slip, Δλ_(i), at each of the n tires of the vehicle from quantities P.sub.φi and P_(yi) dependent on braking forces B_(i) and cornering forces S_(i) and the steering angle δ, and from the deviation of the calculated yaw rate from the actual yaw rate determined in step d) and the deviation of the calculated transverse acceleration from the actual transverse acceleration determined in step e) using the following equation:

    Δλ.sub.i =C.sub.1 P.sub.yi (ΔY-ΔY.sub.F)+C.sub.2 P.sub.φi (Δφ-Δφ.sub.F)            (III)

wherein c₁ and c₂ are predetermined weighting factors for changes in the transverse acceleration and the yaw rate, wherein i designates one of the n tires; and g) changing brake pressures at each tire according to the brake slip changes calculated in step f).
 2. A method according to claim 1, wherein in step f) the calculated brake slip has differential (PD) and integral components (PI,PID).
 3. A method for controlling braking forces at each of n tires of a vehicle during braking to control driving dynamics, said method comprising the steps of:a) making a small change Δδ in steering angle of the vehicle; b) performing a model calculation to obtain a calculated yaw rate Δφ and a calculated transverse acceleration Δy using the following model differential equations:

    Δφ+k.sub.1 Δφ+k.sub.2 Δφ=k.sub.5 ·Δδ                                  (I)

    Δy+k.sub.3 Δy+k.sub.4 Δy=k.sub.6 ·Δδ(II)

wherein k₁ to k₄ are constants and k₅ and k₆ are quantities dependent on vehicle speed; c) measuring an actual yaw rate Δφ_(F) and an actual transverse acceleration ΔY_(F) ; d) comparing the actual yaw rate and calculated yaw rate and determining a deviation of the calculated yaw rate from the actual yaw rate Δφ-Δφ; e) comparing the actual transverse acceleration and the calculated transverse acceleration and determining a deviation of the calculated transverse acceleration from the actual transverse acceleration Δy--Δy_(F) ; f) calculating changes in braking forces, ΔB_(i), at each of the n tires of the vehicle from quantities P.sub.φi ' and P_(yi) ' dependent on braking forces B_(i) and cornering forces S_(i) and the steering angle δ, and from the deviation of the calculated yaw rate from the actual yaw rate determined in step d) and the deviation of the calculated transverse acceleration from the actual transverse acceleration determined in step e) using the following equation:

    ΔB.sub.i =C.sub.2 P.sub.yi ' (ΔY-ΔY.sub.F)+C.sub.2 P.sub.φi '(Δφ-Δφ.sub.F)           (IV)

wherein i designates one of the n tires; and wherein c₁ and c₂ are predetermined weighting factors for changes in the transverse acceleration and the yaw rate, g) changing brake pressures at each tire according to the braking force changes calculated in step f).
 4. A method according to claim 3, wherein in step f) the braking forces have differential (PD) and integral components (PI,PID). 